TWI351479B - Belt-type continuously variable transmission, stra - Google Patents

Description

[Technical Field] The present invention relates to a belt type stepless speed changer, a cross-type (four) vehicle having the belt type stepless speed changer, and the belt type non-segment pressure element. [Prior Art] Prior to this, 'we have known a straddle-type vehicle with a belt-type stepless speed changer: the belt type stepless speed changer has a __ main sheave (driving force from the engine to the "the main sheave") and - a secondary sheave (the driving force is transmitted to the (four) sheave through the belt autonomous sheave). At least the main sheave and the secondary sheave are configured to have an i-belt sleeve directly operative so that the main slot can be changed The ratio of the diameter of the belt loop sleeve of the wheel to the diameter of the belt loop of the auxiliary sheave is adjusted to adjust the gear ratio. ^Eight body. The main sheave usually has a fixed sheave element (hereinafter, the main slot is fixed) ") and - movable sheave element (hereinafter referred to as "main wheel moving element), the movable sheave element is disposed facing the main sheave fixing element and constitutes a belt groove together with the main sheave fixing element The belt groove has a substantially V-shaped cross section and the belt loop is sleeved onto the groove. The main sheave movable member is displaceable relative to the main sheave fixing member in a direction of the rotation axis t, that is, the main The sheave movable element can be used to bring the movable element of the main sheave closer to or away from the main In the direction of the wheel fixing member, the main groove wheel is provided with a cam plate which is disposed facing the side of the main sheave movable member on the side opposite to the side of the main sheave 7L. The cam plate is The manner of extending to the outside in the k-direction direction and closer to the movable element of the main sheave is formed into a tapered shape. A plurality of roller weights are provided on the main sheave movable element] 26150-99122l.d〇, -6 - 1351479 -崎 今日 6 6 6 第 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 096 The movable element and the cam plate __ 起_1 aspect 'the main sheave movement (4) is formed with a plurality of braking portions extending toward the outer portion of the cam plate/knife. The braking portion of the braking portion is on the outer side of the square The position of the maximum displacement. In addition, each of the roller weights typically has a metal weight body and a cover member having a cylindrical or cylindrical shape. The cover member is formed to cover the weight body - Contact the surface of the metal main sheave moving element and the cam plate (specifically , the outer peripheral surface). Almost the "main sheave-like" sub-groove also has a fixed sheave element (hereinafter referred to as "sub-slot wheel fixing m,) and - a movable sheave element (hereinafter " The auxiliary sheave movable member "), the movable sheave (4) is disposed facing the auxiliary sheave fixing member and constitutes a belt groove together with the auxiliary sheave fixing member, the groove having a substantially V-shaped cross section and a belt The sleeve is sleeved onto the groove. The secondary sheave movable element is energized by the spring in a direction in which the belt width is reduced (i.e., in a direction in which the distance from the secondary sheave fixing member is reduced). When the rotational speed of the main sheave is low, the width of the belt groove on the auxiliary sheave is kept small due to the spring supply capability. Because of this, the belt loop of the auxiliary sheave is set to be relatively large. Because of A, the belt is pulled toward the auxiliary sheave, and due to the pulling force, the roller weight is held closer to the side of the rotating shaft, and the width of the belt groove of the main sheave is kept relatively large. Therefore, the gear ratio becomes larger. As the rotational speed of the main sheave increases, the resulting centrifugal force on the roller counterweight also increases. Therefore, when the π & + carving is performed, the main sheave moving element is pushed in the direction in which the main sheave moves to the outer side of the same direction. Because 126150-1000608.doc 1351479 Liu Nian June 1 曰 repair (more) is replacing the page, the main groove wheel ds diameter is added τ and this is asked I, the belt is pulled toward the main sheave side, and the vice The belt loop of the sheave is reduced in diameter. Therefore, as the rotational speed of the main sheave increases (i.e., as the rotational speed of the engine increases), the gear ratio is further reduced. The gear ratio becomes minimum when the roller weight reaches the maximum displacement position (the roller weight is in contact with the braking portion at this position) and the width of the belt groove on the main sheave is reduced to a minimum (hereinafter, The gear ratio in this case is called the "minimum gear ratio". As described above, in the belt type stepless speed changer, as the gear ratio changes, the roller weight is displaced to the inner side in the radial direction and The outer side simultaneously collides with the main sheave movement 70 pieces and the cam plate slides. Therefore, one of the roller counterweights contacts the main sheave movable variable element and the part of the cam plate is deformed with time. Therefore, the roller counterweight is in the face. The width in the direction of the movable element of the main sheave and the direction of the cam ^ decreases with time. Therefore, there is a problem that the width of the belt groove of the main sheave increases with time. That is, there is a problem that the minimum gear ratio changes with time. In view of the foregoing problems, for example, the patent document discloses a technique in which the braking portion is shaped to accelerate wear on a portion of the outer surface of the roller weight. In this technique, when the roller weight is subjected to centrifugal force When pressed on the brake. P, one part of the outer surface of the roller weight is actually worn. Due to this wear, the pressing member buckles the brake portion and moves further to the outside in the radial direction. The width of the belt groove on the main sheave is reduced, thereby changing the gear ratio in a direction in which the gear ratio is reduced. In other words, the wear of the roller counterweight due to wear in contact with the cam plate can be corrected. 1») The wheel ratio is increased. Therefore, the gear ratio change at the minimum gear ratio can be changed by J26150-1000608.doc 1 is 1479 f. The year of the month is repaired (more).

- Simple change of the shape of the brakes only L^^^rirTJ

[Patent Document 1] International Patent Publication No. 2〇〇5/〇9〇828 ai booklet [Summary of the Invention] [Problems to be Solved by the Invention] However, as a result of special research conducted by the inventors of the present application It was initially discovered that the technology revealed by the households in the literature 1 'when there is a crack or break in the covering part = the damage of the covering part is rapidly accelerated, from the shrinkage; the service life of the weight of the decayer. That is, the cover member is typically fixed to the weight body without allowing displacement. However, when a crack or break occurs on the covering member, the covering member is not fixedly fixed to the weight body. Therefore, the roller counterweight cannot smoothly move to the inner side and the outer side in the radial direction, and the cover HH collides with the counterweight main body and other components placed nearby, thereby causing significant damage/this, the roller counterweight The life expectancy is likely to be shortened. • According to the month, the problem is described in the present day and the month, and one of the objects of the present invention is to suppress the gear ratio change and the improved durability of the skin-type stepless speed changer at the minimum gear ratio. [Means for Solving the Problem] - A first belt type stepless speed changer according to the present invention includes a main sheave which rotates about a rotating shaft, a sub-groove wheel and a ring sleeve of the main sheave and the sub-groove Belt. The main sheave has a first sheave element, a second sheave element, a pushing element and a braking portion. The second sheave element faces the first sheave element H sheave element so as to be positionally displaceable in one of the axis directions of the (four) sheave element. The second sheave element and the first wheel member form a belt groove for the belt loop. The pusher element 126I50-991221.doc 1JM479 ------ month w曰 repair (more) is replacing the page, including the pusher member covering the cover member of the body of the pusher. The pressing member rotates around the heart axis of the main groove wheel as the second sheave element rotates. Due to the rotation, the pressing member moves the pressing member toward the first sheave member side in the radial direction of the second sheave member, thereby reducing the belt ο 乐一铭轮The wheel member core - f the brake portion is adjusted by contacting the cover member of the pressing member in the second wheel ratio to minimize the width of the belt groove The positional θ in the radial direction of the second sheave element to the outer side has a surface of the pressing body covered by the covering member that accelerates the wear of the covering portion. The less-portion has a concavo-convex portion including the cover. The one of the jaws is engaged with a raised portion or a recessed portion. The second belt type stepless speed changer according to the present invention comprises: a winding shaft 2' main groove wheel, a pair of groove wheel and a ring sleeve main wheel and the auxiliary groove wheel: the main groove wheel has a first groove a wheel element, a second sheave element, a r-pressing element and a braking portion. The second sheave element faces the first sheave. The second sheave element is positioned to be relatively displaceable in one of the axial directions of the first sheave element. The second sheave element and the first sheave form a belt groove for the belt loop. The urging member includes a pressing member main body and a covering member covering a portion of a surface of the pressing member main body. The pressing member rotates with the α of the second sheave element, and the rotating shaft of the main sheave rotates. Due to the centrifugal force generated by the rotation, the pressing member moves in the radial direction of the second sheave element by 126150-991221.doc 1351479, and the replacement is paged to the outside while facing the The "pilot wheel" element 1 half pushes the two sheave elements, thereby reducing the width of the belt groove. The braking portion adjusts the pressing member by contacting the covering member of the pressing member when the second sheave member reaches the position of the smallest tooth that minimizes the width of the belt groove The displacement of the second sheave element in the radial direction to the outside. The braking portion has a contact surface that is in contact with the covering member of the pressing member, and a projection formed on the contact surface and protruding toward the pressing member: the pressing covered by the money cover member At least the portion of the surface 2 of the surface of the element body has a concavo-convex portion. The concavo-convex portion includes a convex portion or a concave portion that is engaged with the covering member. Shift and at the same time note that the push element can be a roller (i.e., a rotating object), but it can also be a slider (sliding object). Good durability in accordance with the present invention. The gear ratio change at the time of the minimum gear ratio can be suppressed and can be changed. [Embodiment] [Best Mode for Carrying Out the Invention] (First Embodiment) According to the first embodiment, the shape of the braking portion and the roller weight are performed. The shape, and the improvement of the surface shape of a β-knife of the contact covering member of the counterweight main body of the specific weight roller weight, thereby effectively suppressing damage of the covering member. Therefore, the gear ratio change at the time of the minimum gear ratio is effectively suppressed, and the durability is improved = °. Thereafter, the detailed structure of the first embodiment will be described in detail with reference to the phase diagram. Please note that the use of the off-road type two-wheeled motor vehicle shown in Fig.! (as an example of the application of the invention in the cross (four) vehicle auxiliary) explains the first embodiment. However, the root 126150-991221.doc ij) 1479 叼明明 lc0 The repairing (more) replacement of the cross-type of the present invention is not limited to this example, and for example, the straddle type vehicle according to the present invention may be a dual-engine type other than the off-road type. Vehicles (such as 'machine models (ie, small turbine models, light-duty models) double-engined vehicles' or the like). Further, the present invention is applicable to a straddle type vehicle (such as an 'ATV or a snowmobile) that is not a two-wheeled motor vehicle. - Overall Structure of Dual-Motor Vehicle 1 - Fig. 1 is a side view of a two-wheeled motor vehicle 1 according to the first embodiment. First, the overall structure of the two-wheeled motor vehicle 1 will be described with reference to FIG. Note that in the following description, the longitudinal direction and the horizontal direction refer to the direction observed by the driver riding on the seat u. The two-wheeled motor vehicle i has a body frame 2. The body frame 2 is provided with a head S3, a tube 4 extending downward from the head tube 3, and a seat post 5 extending from the head tube 3 to the rear. The head pipe 3 is connected at its lower end to the rear wheel 7 via a front fork 6 and the like, and the arm 8 is pivotally supported at the lower end of the seat post 5 to be attached to the rear wheel 9. A cover 1 covering the body frame 2 is placed above the body frame 2. The seat " is provided slightly opposite the center of the cover 1〇. The engine early 12 is provided between the lower tube 4 and the seat post 5 and supported by the lower tube 4 and the seat post 5. As shown in Fig. 2, the engine unit 12 is a combination unit of the engine 13, a belt type stepless speed change machine (hereinafter referred to as "CVT,,) 14 (refer to Fig. 2), a speed reduction mechanism, and the like. The driving force generated by the engine unit 12 is transmitted to the rear wheel 9 via a power transmitting member (not shown) such as a key belt. Please note that in this embodiment the bow I engine 13 is a single cylinder 4-stroke engine. However, engine 13 can be, for example, a 2-stroke engine or a multi-cylinder engine. 126150-991221.doc -12 - Structure of Engine Unit 12 - Next, the structure of the engine unit 12 will be described with reference to FIG. The engine unit 12 includes an engine 13, a CVT 14, a centrifugal clutch 5, and a speed reduction mechanism 16. Note that the structure of one portion of the speed reduction mechanism 16 is omitted in Fig. 2 for convenience of explanation. The engine 13 is provided with a crankcase 17' - a substantially cylindrical cylinder 18 and a cylinder head 19. The crank case 17 is composed of two cases, which are a first case 17a on the left side and a second case 17b on the right side. The first case 17a and the second case nb are disposed adjacent to each other in the vehicle width direction. The cylinder 18 is obliquely connected to the front of the upper portion of the crankcase 17 (see also Fig. 1). A steam cap 19 is attached to the top end of the cylinder 18. A crank shaft 2 that extends horizontally in the vehicle width direction is housed in the crank case 17. The crankshaft 20 is controlled by the first housing 17a and the second housing 17b via bearings 21, 22. The piston 23 is slidably inserted into the cylinder 18. One end of the link 24 is coupled to the crankshaft 20 side of the piston 23. The other end of the link 24 is coupled to a crank pin 59 disposed between the left crank arm 20a of the crankshaft 20 and the right crank arm 2b of the crankshaft 20. Due to this configuration, the piston 23 reciprocally moves in the cylinder 18 as the crank shaft 2 turns. The cylinder head 19 is formed with a recessed portion 19a connected to the inner space of the cylinder bore 8, and an intake port and an exhaust port (not shown) connected to the recessed portion 19a. Further, the ignition plug 25 is fixedly inserted into the cylinder head 19 such that the ignition portion at the top end is exposed in the recessed portion 19a. > The left side portion of the flying cylinder 18 is provided with a connecting inner side of the crank case 及7 and the cylinder 126150-991221.doc •13· 1351479 The cam chain of the inner side of the 盍19 is replaced by the 匕19 Room 26. The timing chain 27 is provided in the cam chain chamber %°. The timing chain 27 encloses the crankshaft 2〇 and the camshaft 28. With this configuration, the cam shaft 28 rotates in accordance with the rotation of the crank shaft 2〇 to open and close an intake valve and an exhaust valve (not shown). The generator case 30 for accommodating the generator 29 is detachably attached to the left side of the front half of the first case 17a. At the same time, the gearbox 3 1 for storing the cvt 14 is attached to the right side of the second casing 17b. The right side of the second half of the second case 1 7b has an opening. This opening is blocked by the clutch cover 32. The clutch cover 32 is detachably fixed to the second case 17b by a screw 33. The gearbox 31 is formed separately from the crankcase 17. The transmission case 31 is constituted by an inner casing 31a covering the inner side (left side) of the CVT 14 in the vehicle width direction and a casing 3丨b covering the outer side (right side) of the CVT 14 in the vehicle width direction. The inner casing 3 1 a is attached to the right side of the crankcase 17. At the same time, the outer casing 3 1 b is attached to the right side of the inner casing 31a, and the belt chamber 34 is defined by the outer casing 31b and the inner casing 31a and formed. The left end of the crankshaft 20 extends through the first housing 17a and within the generator housing 30. A generator 29 is attached to the left end of the crankshaft 20. More specifically, the generator 29 is provided with a stator 29a and a rotor 29b disposed facing the stator 29a. The stator 29a is fixed to the generator case 3〇 in a manner that does not allow rotation and displacement. Further, the rotor 29b is non-rotatably fixed to a sleeve 35 that rotates with the crankshaft 20. Therefore, the rotor 29b rotates relative to the stator 29a as the crankshaft 20 rotates, thereby generating power. The CVT 14 is housed in the belt chamber 34. The CVT 14 has a main sheave 36 and 126150-991221.doc • 14-1351479 < I— ---- - <〇. On April 1st, the repair (more) replacement page was placed after the main sheave 36. The curve ginseng 20 passes through the second case 17b and the inner case 31a and extends to the belt chamber 34. The right side portion of the crankshaft 20 (strictly speaking, on the right side with respect to the bearing 22) forms a main groove axle 20c. Further, the main sheave 36 is pivotally supported by the sheave shaft 20c. Therefore, the main sheave 36 rotates as the crankshaft 20 rotates. On the other hand, the rear half of the transmission case 31 is provided with a pair of sheave shafts 38 which pass through the inner casing 31a and the clutch cover 32 and which extend into the crankcase 17. The secondary sheave shaft 38 is attached to the clutch cover 32 via a sleeve 39. The auxiliary sheave 37 is pivotally supported by the t t auxiliary sheave shaft 38 in the belt chamber 34. A belt (e.g., (plastic plate) V-belt) 41 is provided with a pair of idler pulleys 37 and a main sheave 36. Therefore, when the main sheave 36 rotates together with the crankshaft 2〇, the torque thus generated is transmitted to the auxiliary sheave 37 via the belt 41. Therefore, the auxiliary sheave shaft 38 rotates together with the auxiliary sheave shaft 37. The rotation of the sub-slot shaft 38 is transmitted to the rear wheel 9 via the centrifugal clutch 15, the reduction mechanism 16, and a power transmission mechanism (not shown) such as a belt and a chain. The specific structure of φ - CVT 14 . The structure of CVT 14 will be described in detail below with reference to FIG. As described above, the CVT 14 is provided with the main sheave 36, the auxiliary sheave 37, and the belt 41 and is housed in the belt chamber 34. The main sheave 36 has a fixed sheave element 36& and a movable sheave element 36b, each of which has a tapered shape. The fixed sheave element 36a is fixed to the right end of the main sheave shaft 2〇c so as to extend outward in the radial direction and to approach the outer side (right side) in the vehicle width direction. Further, the fixed sheave element 36a rotates together with the main sheave shaft 2〇c. At the same time, the movable sheave element 36b is positioned such that it faces the fixed sheave element at a position relative to the fixed sheave element 126150-l00Q608.doc 15 1351479 (8) June (more) positive replacement page 1 3 6 a 'Patent Application Replacement Page No. 096142581 (June 1st) The piece 36a is closer to the center (left side) and extends to the outside in the radial direction and is closer to the inside in the vehicle width direction (left side ). The movable sheave element 36b is not rotatably but axially slidably attached to the main sheave shaft 2〇c. That is, the fixed sheave element 36a and the movable sheave element 36b form a belt groove 36c having a substantially cross-sectional shape and a belt 41% fit into the belt groove. The width of the belt groove 3 core can be varied by the relative displacement of the movable sheave element 36b relative to the fixed sheave element 36a. The outer side of the fixed sheave element 36& (the right side in Fig. 2) is provided with a cooling fan 46. One of the left side faces of the movable sheave element 361) is provided with a plurality of cam faces 42, each of which extends in the radial direction. The cam plate η is disposed on the left side of the movable sheave element 36b in such a manner as to face the cam surface 42. A plurality of roller weights ((four) elements) 44 are provided between the cam plate 43 and the cam_. The plurality of roller weights (pushing members) 44 are formed in a substantially cylindrical shape (or - substantially cylindrical shape) and are displaceable in the radial direction but are not displaceable in the direction of rotation. The cam surface 42 is formed in a tapered shape in such a manner as to extend from the center to the outside in the radial direction and close to the cam plate 43. Further, the cam plate 43 is also formed in a heterogeneous shape so as to extend from the center to the outside in the radial direction and close to the :: face 42. That is, the width between the cam plate 43 and the cam surface 42 decreases toward the outer side in the radial direction. The sheave 37 is provided with a fixed sheave member 37a located on the inner side in the vehicle width direction and a vehicle placed on the outer side of the vehicle and facing the fixed sheave member 37a. The movable sheave element "^ is close to the inside in the direction of the width of the solidification (the left side is 2·70 7a to be fixed to the auxiliary sheave shaft 38 in the vehicle mode and 126150-I000608.doc • 16 - 1351479 is replaced by the next year (more) The rotation is extended in the radial direction. At the same time, the movable sheave element 37b is fixed to the auxiliary sheave shaft 38 in the vehicle width direction toward the outer side (right side) and extends to the outer side in the radial direction. The sheave element 37b is not rotatably but axially slidably attached to the sub-slot axle 38. That is, the fixed sheave element 37& and the movable sheave element 37匕 form a belt groove 37c having a large body The cross section of the upper ¥ shape and the belt "loops over the groove of the belt. The width of the belt groove 37 can be changed by the relative displacement of the movable sheave element 37b relative to the fixed sheave element 37a. Please note that the fixing groove The shaft center portion of the wheel member 37a is formed into a cylindrical shape The movable collar is engaged with the auxiliary sheave shaft 38 by a pin groove. The compression coil spring 45 is provided on the outer side (right side) of the movable sheave element 37b in the vehicle width direction. The compression coil spring 45 energizes the movable sheave element 37b. To face the fixed sheave element 37a. Therefore, when the engine rotational speed is low (for example, 'idle state'), the width of the belt groove 37c is the smallest. In the CVT 14, the gear ratio is pressed by the main sheave movable member 36b. The force generated by the roller weight 44 to the main sheave fixing member 36a (to the right) and the compression coil spring energizing the auxiliary sheave movable member 37b toward the auxiliary sheave fixing member 3 (to the left) The ratio between the forces generated by 45 is determined. More specifically, when the rotation speed of the main sheave shaft 2〇c is low, the width of the belt groove 37c of the auxiliary sheave 37 is due to the supply capacity of the compression disc. Decrease (refers to the state (the position of the maximum gear ratio) when the sub-groove 37 is located above the sub-slot wheel batch as illustrated in Fig. 2t.) Therefore, the diameter of the belt loop of the auxiliary sheave 37 is increased, and the belt 41 is Pulling toward the auxiliary sheave 37. Due to this, the main sheave movable jaw 36b is pressed by the belt 41 The cam plate 43, thereby increasing the width of the main groove wheel % 126150-99122I.doc -17- Μ 月 曰 ( ( 正 正 正 正 正 正 ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( The state in which the main sheave 36 is located below the main sheave shaft 20c (the position of the maximum gear ratio). As a result, the gear ratio is increased. χρ, aspect 'When the rotational speed of the main sheave shaft 20c increases, the roller counterweight 44 By the centrifugal force of the fork and moving to the outside in the radial direction, in this case, the distance between the main sheave movable element 36b and the cam plate 43 decreases as it moves toward the outer side in the sexual direction. Therefore, as a result of the roller weight 44 moving to the outside in the direction, the main sheave movable member 36b is fixed to the main sheave fixing member 36a (to the right). Thus, the main sheave moving element is sinned toward the main sheave fixing member 36a, and thus the belt groove 36c is changed (the state in which the main sheave 36 is located above the main sheave axis as illustrated in FIG. 2) (the position of the smallest gear ratio)). Therefore, the diameter of the belt loop of the main sheave is increased. At the same time, the belt 41 is pulled toward the side of the main sheave 36, and the belt 41 pushes the sub-groove activity in a direction away from the auxiliary sheave fixing member 37a (to the right) of the compression coil spring 45. Element 3. Therefore, the auxiliary sheave movable member (4) slides in a direction away from the auxiliary sheave fixing member 37a, thereby reducing the diameter of the belt loop of the auxiliary sheave 37 (refer to that the auxiliary sheave 37 as illustrated in FIG. 2 is located in the auxiliary groove The state under the axle 38 (the position of the minimum gear ratio)). As a result, the gear ratio becomes smaller. Please note that (4) for the main sheave fixing member 36a, the main sheave movable member 36b, the auxiliary sheave fixing member 37a, and the auxiliary sheave moving members ^ and 43 are not specifically limited, and for example, the material may be Typical examples of metals are iron, aluminum, steel materials and the like. Eight Surface treatment such as chrome plating is applied to the surface. I26150-99I221.doc 1351479 ‘· Μ Μ 修正 修正 修正 此外 ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ ’ 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 Therefore, the roller weight can be any member as long as it can move to the inner side and the outer side in the radial direction. For example, the roller weight 44 can be a sphere shape, a bag shape, and the like. Additionally, the roller weight 44 can be an object that moves while rotating or can be a sliding object. - Structure of the main sheave 36 and the roller counterweight 44 -

Hereinafter, the structure of the main sheave 36 and the roller counterweight 44 according to the first embodiment will be described in detail with reference to Figs. First, the structure of the main sheave movable member 36b will be described in detail with reference to Figs. <Structure of Main Slot Moving Member 36b> Fig. 3 is a rear view of the main sheave movable member 36b as viewed from the intermediate portion in the vehicle width direction. A plurality of guiding portions 51 are formed on the back surface of the main sheave movable member 3, and the roller counterweights 44 are disposed in the guiding portions. More specifically, the six guiding portions 51 are radially formed in such a manner as to extend from the convex portion 50 to the outer side in the radial direction, respectively. The six guiding portions (four) are formed into three pairs of guiding portions & each pair includes two adjacent guiding portions 5 arranged in a V shape, and the three pairs of guiding portions are disposed around the protruding portion 50 at substantially equal intervals . Each of the guiding portions 51 includes a cam surface 42 and a pair of guiding walls 52a and 52b. As shown in Fig. 2, the cam_ extends to the outside in the warp direction while being inclined toward the cam plate 43 side. As shown in Fig. 4, each of the lead wall and the Mb protrudes parallel to each other and protrudes along the cam::: = in the radial direction. The distance between the guide wall 52a and the guide wall 52b is set to be the same as that of the = 126J50-991221.doc •19· 1351479 Η2·month u»日冲正正页重重重44 44 1 guides the j portion 5 1 to be displaced along the guide walls 52a and 52b in the radial direction.

The outer end of each of the guiding portions 51 in the radial direction is provided with a braking portion 53 which protrudes from the cam surface 42 toward the cam plate 43 side (see also Fig. 2). The braking portion 53 confirms the outer end in the radial direction of the possible range of movement of the roller weight 44. More specifically, when the main sheave movable member 36b is positioned at the position of the smallest gear ratio that minimizes the width of the belt groove 36c, the main sheave movable member 36b contacts the roller counterweight 44 (specifically, the roller is matched One of the weights 44 covers the component magazine, thereby adjusting the further displacement of the roller weight 44 to the outside in the radial direction. As shown in Fig. 3, one of the braking portions 53 is in contact with the roller weighting material. The face 54 is formed into a shape that causes the wear on one of the outer surface of the roller weight (in particular, the cover member 44a) to be actively accelerated. More specifically, as shown in FIGS. 5 and 6, the main The substantially central portion of the sheave 36 in the radial direction is provided with a linear convex portion 55 having a rectangular cross section and protruding toward the roller weight 44. As shown in Fig. 7, the convex portion 55 is fitted with the roller. weight

The outer surface of the 44 is in contact with each other to thereby accelerate the wear on the contact portion compared to other portions. The history is covered by the braking of the covering parts. In this manual, ***- -I · I ΊΜ & & quot 〇 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指 指The other part of the surface pressure is divided into two parts, in which case the pushing element (roller 酉 or the like) is new. More specifically, in the first embodiment,! One of the parts 4 4 a Λ Λ plus eight w , "the portion of the raised Deng knife 55 contacting corresponds to the portion of the portion of the brake portion of the wear d cover member." <Structure of the roller weight 44 ; 126150-99l221.doc •20- 1351479 Issued ¥X Yue repair (more) positive view. 1 崮8(b)A >/riv

Figure 8 (a) shows the roller weight 44 ^ 1 ϋ ^. Fig. 8(b) is a view taken at the line Vm(b)-vm(b) marked by the arrow in Fig. 8(a). The roller weight 44 has a line-shaped official weight main body 44b made of metal such as iron, stainless steel or the like, and a covering member 44a covering the outer peripheral surface of one of the weight main bodies 44b. Note that the weight main body 44b is not necessarily made of metal. However, in order to generate a specific level of centrifugal force, the weight body 4 should preferably have a specific level or a higher level of specific gravity. Further, the covering member 44a should preferably have a lower hardness than the weight main body 4. More specifically, the 'cover member 44a' should preferably be made of a resin. In the first embodiment, the outer peripheral surface 4 c covered by the covering member 4 is. The minute (or possibly all) has a concavo-convex portion including a convex portion or a concave portion that is engaged with the covering member 44a. The outer peripheral surface 44c covered by the cover σ member 44a is formed to have a rough surface having a fine concave shape and a convex shape.

a smooth flat surface or a rough surface, a concave surface or a convex surface (the surface shape of which may be a rough surface or a smooth surface) of a concave portion or a convex portion, or a recessed portion Or a concave surface or a convex surface of one part of the portion of the slab (the surface shape of which may be a rough surface or a smooth surface). More specifically, in the first embodiment, the integral outer peripheral surface 44c is formed to have a rough surface. Note that the method of forming the outer peripheral surface 44c such that it has a rough surface is not particularly limited, and for example, the method may be a mechanical processing method using sandblasting or knurling or an etching or the like Representative chemical processing methods. 126150-991221.doc • 21 · The year of the next year (more) is replacing the thickness of the page covering member 44a and the thickness of the portion of the contact portion 55 that is in contact with the convex portion 55 is set to be larger than the convex portion 55 is at the height of the direction of the main: wheel 36 (see Figure 5). More specifically, the thickness t of the cover member 44a is set to be larger than the height η of the convex portion 55. (7) The thickness t of the cover member 44a is preferably set to be larger than the outer circumference of the roller weight 44. The radius is at least one percent larger. - Operation and Effect - The operation and effect of the first embodiment will be described with reference to Figs. 9 to 12. Fig. 9 and Fig. 1G illustrate a state in which the movable sheave element of the main sheave % is moved to the position of the minimum gear ratio via the new roller counterweight 44. In this state, the covering member 44a of the roller weight 44 is in contact with the cam plate 43, the convex portion 55, and the cam surface 42. When a portion of the covering member 44a that is in contact with the cam plate 仏 and the four-wheel face 42 starts to wear, the distance between the cam plate 43 and the cam surface 42 decreases. At the same time, the width of the belt groove We of the main sheave is increased, which reduces the diameter of the belt loop. Therefore, the minimum gear ratio becomes smaller than when the present invention is not used. The towel, i.e., due to the wear of the portion of the cover member 44& which is in contact with the cam plate 43 and the cam surface 42, the minimum gear ratio changes with time. According to the first embodiment, when the movable sheave element 36b is slid to the position of the minimum gear ratio, the convex portion 形成 formed on the braking portion surface 54 comes into contact with the covering member 44a of the roller weight 44. Therefore, the surface pressure of a contact portion 36{} of the covering member 44a which is in contact with the projection 4 blade 55 becomes larger than the surface pressure of the other cutters. Further, the covering member is made of a material having a relatively low hardness (specifically, a resin). Therefore, compared with the other parts, 126150-991221.doc •22·1351479, last year, from the Japanese goods, the replacement of the page ratio, the contact portion 36d is actively ground---FIG. 11 and FIG. 12 illustrate the contact portion of the cover member 44a. 36d has been partially worn. As shown in Figs. 11 and 12, due to the partial wear of the contact portion 36d, a recessed portion 36e having a shape corresponding to the shape of the convex portion 55 is formed, and the convex portion 55 is inserted into the covering member 44a. As a result, the roller weight 44 is moved in the radial direction of the movable sheave element 36b to the outer side corresponding to the amount of the convexity of the convex portion 55. Therefore, the width of the belt groove 36c is reduced, and the diameter of the belt loop of the main sheave 36 is increased. That is, the reduction in the diameter of the belt loop caused by the abrasion of the portion of the cover member _ 44a which is in contact with the cam plate 43 and the cam surface 42 is caused by the increase in the diameter of the belt loop due to the wear of the contact portion 36d. Correction. As a result, the time variation of the gear ratio with respect to the rotational speed of the main sheave shaft 20c and the temporal change of the minimum gear ratio are effectively suppressed. Nevertheless, the depth of the recessed portion 36e increases as the wear of the contact portion 36d is intensified, and thus there is a possibility that the covering member 44a is cracked at the center of the recessed portion 3. In addition, there is also a possibility that the recessed portion 36e will reach the weight main body 44b as the wear is further intensified. In this case, the roller weight 44 does not smoothly move to the inner side and the outer side (looseness) in the radial direction, and thus the covering member 44a collides with or strongly rubs against the weight main body 44b, the cam plate 43 and the like located nearby. Thereby causing significant damage. As a result, the service life of the roller weight 44 is shortened. According to the first embodiment, the portion of the weight main body 4 covered by the covering member 44a, which complements the outer peripheral surface 44c (and more specifically, the face that engages with the covering member 4), is formed to have a rough surface. Therefore, even in the case where the cover 126l50-99l22I.doc -23·1351479 9 beer repair (£) is replacing the purchase of the part 44a to generate a crack or the recessed portion 36e reaches the weight main body 44b, the cover member 44a is still borrowed. The fixing to the weight main body 44b is maintained by the frictional force between the outer peripheral surface 44c of the weight main body 44b and the inner peripheral surface of the covering member 44a. Therefore, the roller weight 44 is not affected to smoothly move to the inner side and the outer side in the radial direction, and the damage of the covering member 44a is suppressed. Therefore, the durability of the belt type stepless speed changer]4 is increased. Further, in the first embodiment, the thickness t (see Fig. 8(b)) of the covering member 44a is set to be larger than the height H of the convex portion 55 in the radial direction of the main sheave % (refer to Fig. 5). Therefore, even when the convex portion brother has been inserted into the covering member 443, the depressed portion he does not reach the weight main body 44b. Therefore, this structure makes it difficult to form cracks or cracks on the covering member 44a. Further, in order to effectively suppress cracks or cracks in the covering member 44a, the thickness (1) of the covering member 44a is particularly preferably set to be larger than 凸起1 mm than the height of the convex portion. Further, the thickness of the covering member 【 is particularly Preferably, it is set to be at least 7% greater than the outer circumferential radius of the roller weight 44.

Hereinabove, the example of the first preferred embodiment to which the present invention is applied has been described. The part of the surface of the 'weighted body 44b' covered by the covering member 4 (that is, the 'outer peripheral surface 仏) is not necessarily the thick-chain surface, that is, the surface of the 'weighted body 44b' The upper part is covered by the covering member 44 & (i.e., the outer peripheral surface 44c), but the y-knife must have a raised protrusion having a covering member 44a. The concavity and convexity of the P-knife or a recessed portion makes it possible to cause cracks or the like in the _*^ A in the covering member 44a. The I5 member 44a is still fixed to the fitting body 441. More specifically, the outer peripheral surface 44c can be JL times u. P. Eight one or more concave portions or convex portions. 126150-991221.doc -24· 1351479 . ^ Patent application No. 096142581 ____ —_ = replacement of the book _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ 'to the summer to the main; ^ the axle 2 〇 (the portion of the ? / / into the concave shape (preferably, the lowest point perpendicular to the portion of the main sheave shaft 20c facing the cover member 44a and the convex portion 55 The portion to be contacted. ^ In the following - and the second embodiment, an example in which the depressed portion is formed on the outer peripheral surface 44 is described. Note that the second and third embodiments are described with reference to FIG. 7 to 8(a), 9 and 9. In addition, reference numerals (4) in the first embodiment are used for structural elements having substantially the same function, and thus descriptions of the elements are omitted. (Second Embodiment) Fig. 13 is a cross-sectional view of a roller weight 144 according to a second embodiment. Fig. 14 is a view showing a relationship between the roller weight 144 and the convex portion 5 of the braking portion 53 according to the second embodiment. A schematic plan view of the positional relationship. The roller g 144 according to the second embodiment includes a metal weight body 144b formed into a cylindrical shape. a cover member M4a. The outer peripheral surface 144c of the weight body has a plurality of (specifically, two) annular grooves # each of the annular grooves has a rectangular cross-sectional surface and is in the direction of rotation More specifically, as shown in Fig. 14, a portion of the cover member 与 which is in contact with the convex portion 55 (the portion where the wear is accelerated by the braking portion 53) is located between the two annular grooves 144d. 14牦 is formed in such a manner as to cover the outer peripheral surface 144cJ_ of the weight body 144b inserted into the two annular grooves 144 (i formed on the outer peripheral surface 144c. As described above, due to the covering member 144a and the annular groove 14 The cymbal is engaged, and the portion of the covering member 44a that is in contact with the convex portion 55 is located between the two annular grooves 144d', so even at the 126150-1000608.doc-25 due to the friction with the convex portion 55 · 1351479, June, 2010? In the case of daily replacement (more) replacement of the weight body (4)b in the sheet covering member 144a, the covering member 144a remains fixed to the weight body 14. Therefore, the roller is not affected. Counterweight 144 smoothly moves in the radial direction The damage to the inner side and the outer side 'and the covering member 144a is suppressed. In order to effectively suppress the crack or crack of the covering member 14, the thickness of the portion of the covering member M4a in contact with the convex portion 55 is set larger than the convex portion 55. The height, and furthermore, the thickness is preferably set to be at least i mme larger than the height of the convex portion 55. Further, the thickness of the portion of the covering member M4a that is in contact with the convex portion 55 is preferably set to be larger than the roller weight. * The outer circumferential radius is at least a large percentage... Note that the outer peripheral surface (10) of the 'weighting body 144b' may be formed as a rough surface as in the first embodiment. As described above, in the second embodiment, an example in which the two annular grooves 丨4 are cut into the outer peripheral surface 14 of the weight body 144b is described. However, the invention is not limited to the structure in this example. The present invention can take any form as long as the covering member 144a is formed in a manner of snapping engagement with the outer peripheral surface 14. For example, three or more annular grooves 144d may be formed. Further, the recessed portion formed on the outer peripheral surface of the weight body 144b is not necessarily annular. Further, one or more convex portions (for example, 'annular convex portions') may be formed instead of the annular groove 14''. (Third Embodiment) Fig. 15 is a cross-sectional view of a roller weight 244 according to a second embodiment, and Fig. 6 is a view between the roller weight 244 and the convex portion 55 of the braking portion 53 according to the second embodiment. Schematic plan view of the positional relationship. Figure 17 is a diagram illustrating the roller weight 126150-1000608.doc -26- 1351479 • Patent No. 096142581----一·^ Chinese manual replacement page (June 100) Year of the furnace 6 The monthly replacement page 244 is inserted into the pan state of the braking portion 533⁄4, such as the J1 view. As shown in Fig. 15, the 'roller weight 244 has a metal weight formed into a cylindrical shape. The main body 244b and a covering member 244a. The outer peripheral surface 244c of the weight main body 244b is provided with an annular groove 244d having a rectangular cross section and extending in the direction of rotation. The annular groove 244d is formed at a position (lower) In this article, 'this location can also be called "correspondence The position ") of the convex portion 55 is substantially at the center of the axial direction of the weight main body 244b and faces a portion of the covering member 244a that is accelerated by the braking portion 53 (covering and bulging of the member 244a) The portion where the portion 55 is in contact.) The depth (d2) of the annular groove 244d is set to be larger than the height of the convex portion 55 by at least 1 mm. Further, the width (W2) of the annular groove 244d is set to be larger than the convex portion. The width (W1) of the portion 55 is wide such that when viewed in the radial direction of the autonomous sheave 36, the portion of the covering member 244a that is in contact with the convex portion 55 is included in a portion perpendicular to the main sheave shaft 20c. That is, the annular groove 24 is cut to be wider than the convex portion 55. The covering member 24 is formed to cover the outer peripheral surface 244c of the weight main body 244b and inserted into the annular groove 244d formed on the outer peripheral surface 244c. In other words, the covering member 24 is provided with an annular convex portion that extends into the weight main body 244b and is inserted into the annular groove 244d. Therefore, as shown in Fig. 17, even when the covering member (10) rubs the convex portion 55 and is convex section When the 55 is inserted into the covering member 244a, the tip end of the convex portion 55 still does not reach the outer peripheral surface _ of the weight main body 。. Therefore, cracks are not easily generated in the covering member 244a, or breakage is unlikely to occur. Inserting the convex portion 55 into the covering member (10) and 126l50-I000608.doc -27- 1351479 π年έ月?日修(more) replacement page is cracked or broken in the covering member 244a, as shown in Fig. 17 It is shown that the first convex portion 255a and the second convex portion 255b which are separated from the convex portion 255 of the covering member 244a are still engaged with the annular groove 244d on the weight main body 244b, respectively. Therefore, the covering member 244a is held fixed to the weight body 244b. Therefore, the roller weight 244 is not affected to smoothly move to the inner side and the outer side in the radial direction, and the damage of the covering member 244a is suppressed. Further, in the present embodiment, the width (W2) of the annular groove 244d is set to be wider than the width (W1) of the convex portion 55. Therefore, even when the wear of the covering member 244a is further aggravated and the convex portion 55 reaches the weight main body 244b, the first convex portion 255a and the second convex portion 255b are still present. Therefore, even if the convex portion 55 reaches the weight main body 244b, the covering member 244a remains fixed to the weight main body 244b. Therefore, the roller weight 244 is not affected to smoothly move to the inner side and the outer side in the radial direction, and the damage of the covering member 244a is suppressed. As described above, the annular groove 244d is formed at a position on the surface of the weight main body 244b corresponding to the convex portion 55, and the thickness of the portion of the covering member 244a is increased. Due to this configuration, cracks or breakage are less likely to occur in the covering member 244a, and the convex portion 55 does not easily reach the weight main body 244b. Meanwhile, for example, as a method of covering the thickness of the member 244a at the position corresponding to the convex portion 55 on the weight-increasing body 244b, in addition to forming the annular groove 244d, it is also possible to increase the total thickness of the covering member 244a. Nevertheless, in this case, the volume capacity of the weight main body 244b is reduced as compared with the case of the third embodiment, thereby causing a problem that the weight of the roller weight 244 is reduced. In contrast, according to the method of forming the ring 126150-1000608.doc -28-1351479 in the present embodiment, the β groove is 244d, the page groove 244d is being replaced, and the maximum capacity can be reduced' and can be increased. The thickness of the weight main body 2 at the position corresponding to the convex portion 55 of the peach upper covering member 244a. Note that also in the third embodiment, as in the first embodiment, the outer peripheral surface of the weight body is formed - it can be formed as a raw sugar surface. Further, as in the second embodiment, one or more annular grooves (or annular convex portions) may be further formed on both sides in the axial direction of the roller weight 244.

Hereinabove, the first to third embodiments to which the present invention is applied are described. However, the braking portion 53 is not limited to the example in which one convex portion 55 is formed on the moving surface 54. For example, the 'brake portion 53' may be formed on each of the two ends of the braking portion surface 54a of the braking portion 53a in the axial direction of the material weight 44 as shown in FIG. . In addition,

The face can be formed as a convex face that protrudes toward the roller weight. In the following modified example, an example in which the braking surface is formed as a convex surface will be described. Note that, in the description of the modified examples below, the same reference numerals as in the embodiments to the third embodiment are used for the structural elements having substantially the same functions, and thus the description of the elements is omitted. Further, as in the first embodiment, reference is made to Figs. 1 and 2. (Modified Example) Fig. 19 is a schematic view for explaining the shape of the braking portion 53b in the modified example. In this modified example, the braking portion surface 54b of the braking portion 53 is formed as a convex surface that protrudes toward the roller weight 344. Further, in this configuration, as in the case of the first embodiment, the wear on the portion of the cover member 34 of the roller weight 344 which is in contact with the top portion of the braking portion 54b is added by 12615 〇 - 99l221 .d. -29· 1351479 I”卞, L月to曰 repair (more) is replacing the page speed. Therefore, the belt pulley of the main sheave 2 is straightened, and therefore, the cover member 344a and the cam plate 43 and the cam The reduction of the belt loop straightness caused by the wear of the portion in contact with the face 42 is corrected. Therefore, the time variation of the gear ratio with respect to the rotational speed of the main sheave shaft 20c and the time variation of the minimum gear ratio are effectively suppressed. In the G modified example, the roller weight 344 has a weight body 344b and a covering member 344a. The outer peripheral surface 344 of the weight body 344b is formed as an axial portion of one of the weight bodies 344b. The inner peripheral surface of one of the covering members 344 & is formed as a convex surface and is engaged with the outer peripheral portion of the weight main body 344b. The outer peripheral surface 344 of the weight main body side is perpendicular to the main sheave shaft 2 ( The lowest point at the part of ^ The apex of the braking portion surface 54b in the radial direction of the main sheave 36. Thus, as in the third embodiment, this structure makes the thickness of the portion of the covering member 344a in contact with the apex of the braking portion surface 54b relatively relatively Therefore, the apex of the braking portion surface 54b does not easily reach the outer peripheral surface of the weight main body. Therefore, the crack generation in the covering member 344a and the breaking of the covering member 344a are effectively suppressed. The thickness of the portion where the apex of the moving portion surface 54b contacts is further increased, and the radius of curvature of the outer peripheral surface of the weight main body 344b is preferably larger than the radius of curvature of the brake 54b. Further, even when the covering member 344a is split into two portions Next, each of the two split portions of the cover member 344a is still engaged with each other. Therefore, the cover member (10) is fixed to the weight 3 peach. Therefore, the roller weight 344 is not affected. Smooth movement in the direction 126150-991221.doc • 30 - 1351479 • . :· %曰修(more) is replacing the page, and the cover part 34: ^ damage system $ 明 is effectively applied to belt type without section change The straddle type vehicle of the machine is light. In detail, the present invention effectively occupies the straddle type vehicle of the belt type stepless speed changer having a relatively large displacement. [Simplified illustration] FIG. 1 is based on Side view of the two-wheeled motor vehicle of the first embodiment. Fig. 2 is a cross-sectional view showing the structure of the engine unit.

Fig. 3 is a plan view showing the main wheel member viewed from the intermediate portion in the vehicle width direction.曰 圊 4 is a view taken along line IV_IV marked with an arrow in Fig. 3. Fig. 5 is an enlarged cross-sectional view of the braking portion according to the first embodiment. Fig. 6 is a view taken along line νι_νι marked with an arrow in Fig. 5. Fig. 7 is a schematic plan view showing the positional relationship between the roller weight and the convex portion of the braking portion according to the first embodiment.

To the inside and outside [Industrial Applicability] Figure 8 (a) is a perspective view of the roller weight. Fig. 8(b) is a view taken along the line VlII(b)_VIII(b) marked with the arrow in Fig. 8(4). Fig. 9 is a cross-sectional view of the main sheave], which illustrates a state in which the new roller weight is in contact with the convex portion of the braking portion in the first embodiment. Fig. 10 is a view taken along line χ·χ marked with an arrow in Fig. 9. Fig. 11 is a cross-sectional view of the main sheave, which illustrates a state in which the roller weight is inserted into the convex portion 10 of the braking portion in the first embodiment. Fig. 12 is a view in which /α is taken by a line ΧΙΙ-ΧΙΙ indicated by an arrow in Fig. 11. Figure 13 is a cross-sectional view of a roller weight according to a second embodiment. ]26150-99 ] 221 .doc -31- 1351479 tj 啊久月> 日修(more) replacement page Fig. 14 is a description of the convex portion of the roller weight and the braking portion according to the second embodiment The schematic plane of the positional relationship between the two. Figure 5 is a cross-sectional view of the roller weight according to the third embodiment. Fig. 16 is a schematic plan view showing the positional relationship between the roller weight and the convex portion of the braking portion according to the third embodiment. Fig. 17 is a cross-sectional view of the main sheave, which illustrates a state in which the roller weight is inserted into the convex portion of the braking portion in the third embodiment. Fig. 18 is a schematic view showing a change in the shape of the braking portion. Fig. 19 is a schematic view showing the shape of a braking portion according to a modified example. [Main component symbol description] 1 Double-wheeled motor vehicle 2 Body frame 3 Head tube 4 Lower tube 5 Seat column 6 Front fork 7 Front wheel 8 Rear arm 9 Rear wheel 10 Cover 11 Seat 12 Engine unit 13 Engine 14 Belt type without section change

Lost (CVT) 126150-991221.doc • 32 · 1351479, year-to-month w-day repair {more) replacement page

15 Centrifugal clutch 16 Retarder 17 Crankcase 17a First case 17b Second case 18 Cylinder 19 Cylinder head 19a Recessed part 20 Crank unit 20a Left crank arm 20b Right crank arm 20c Main groove wheel shaft 21 Bearing 22 Bearing 23 Piston 24 Connecting rod 25 Ignition plug 26 Cam chain chamber 27 Timing key 28 Camshaft 29 Generator 29a Stator 29b Rotor 30 Generator shell 126150-991221.doc -33- 1351479 Leap year ΐ ί ί ί 替换 31 31 31 Gearbox 31a Inner casing 31b Housing 32 Clutch cover 33 Screw 34 Belt chamber 35 Sleeve 36 Main sheave 36a Main sheave fixing member 36b Main sheave movable member 36c Belt groove 36d Contact portion 36e Recessed portion 37 Sub-groove 37a Slot fixing element 37b Sub-groove moving element 37c Belt groove 38 Sub-slot shaft 39 Bearing 41 Belt 42 Cam surface 43 Cam plate 44 Roller weight 44a Covering part 126150-991221.doc •34 1351479 ·

Today 1 year I i month (1) day repair (more) replacement page 44b counterweight body 44c outer peripheral surface 45 compression coil spring 46 cooling fan 50 projection portion 51 guide portion 52a guide wall 52b guide wall 53 brake portion ' 53a Brake 53b Brake 54 Brake face 54a Brake face 54b Brake face 55 Projection 55a Projection 59 Crank pin 144 Roller weight 144a Covering member 144b Counterweight body 144c External peripheral surface 144d Annular groove 244 Roller weight 244a Covering parts 126150-991221.doc -35· 1351479 244b 244c 244d 255 255a 255b 344 344a 344b 344c d2 H t W1 W2 year alpha month π day repair (£) is replacing page weight master "&quot ; outer peripheral surface annular groove annular convex portion first convex portion second convex portion roller weight covering member weight main body outer peripheral surface annular groove 244d depth convex portion 55 height cover member 44a thickness The width of the convex portion 55 is the width of the annular groove 244d 126150-991221.doc • 36·

Claims (1)

1351479 __ Patent application No. 96142581 Chinese patent application scope replacement (100 years June) X. Patent application scope: A belt-type stepless speed-shifting machine, which has a main sheave that rotates around a rotating shaft, a pair of sheaves, and a long sleeve of the main sheave and the pair of sheaves, wherein. * The main sheave includes: a first sheave element; the first sheave 70 member 'which faces the first sheave element in such a manner as to be relatively displaceable in the axial direction of the first sheave element Arranged, and I, the first sheave element together form a belt groove for the belt loop sleeve; and a push 7L member, comprising - pushing the element body and - covering the body of the push π member - a covering member of at least a portion of the surface, the pressing member rotates about the rotating shaft as the second sheave member rotates, and the centrifugal force generated by the rotation of the pressing member The pressing member moves toward the outer side of the shuttle gear member in the shuttle direction and simultaneously pushes the second sheave member toward the first sheave member side, thereby reducing the width of the belt groove, and braking 4, #纟 the second sheave element reaches a minimum gear ratio that minimizes the belt groove=width Receiving contact with the cover member of the pressing member and restricting displacement of the pressing member to the outer side in the technical direction of the third sheave member, wherein the braking portion has a portion of the covering member a shape accelerated by wear, and a portion of the surface of the pressing member main body covered by the covering member to the J- portion is provided with a concave-convex portion including one of the components 126150-1000608.doc 2. The raised portion h is, for example, the year of the valley, the Japanese repair (the phantom replacement page | the recessed] HF seed skin ▼ type stepless speed changer, which has a main sheave, a sub-groove and a loop sleeve rotating around a rotating shaft a main sheave and a belt of the secondary sheave, wherein the main sheave comprises: a first sheave element; a first sheave element that is relatively displaceable in the axial direction of the first sheave element The method is disposed facing the first sheave element, and together with the/the second sheave element, forms a belt groove for the belt loop sleeve; the pushing element comprises a pushing element body and a covering body One of the body of the pressure element is +r, the surface is up to >, a part of the covering member, the pushing element is rotated about the rotating shaft by the rotation of the first sheave element, and the pressing force is generated by the centrifugal force generated by the pressing of the pressing member The side of the first sheave element is moved outwardly in the direction of the direction and simultaneously urges the second sheave element toward the first sheave element side, thereby reducing the degree of the belt groove; and '-braking portion, where The second sheave element reaches the position of the smallest gear ratio that minimizes the width of the belt groove and is in contact with the covering member of the pressing member, and limits the diameter of the pressing member to the second sheave member Displacement toward the outer side of the direction, wherein the braking portion has a contact surface that is in contact with the covering member of the pressing member and a convex portion formed on the contact surface and facing the pressing member, and the dog is pushed out The portion of the surface of the pressing member main body covered by the covering member is 126150-1000608.doc π years δ month, and the daily repairing (more) positive replacement page has at least a portion having a d convex portion. 'The concave and convex portion includes a card with the covering member One convex part A recessed portion. 3. The belt type stepless speed changer of claim 1 or 2, wherein two or more concave and convex portions are formed, and a portion of the covering member that is accelerated by the braking portion is located in a circumferential direction of the main sheave Between the two or the two or more concave and convex portions. 4. The belt type stepless speed changer of claim 1 or 2, wherein a recessed portion that engages with the covering member is formed in a front surface of the pressing member body in a radial direction of the main sheave The cover member is accelerated by the braking portion at a position where one of the worn portions is worn. 5. The belt type stepless speed changer of claim 4, wherein the recessed portion is formed to include the wear portion and is wider than the wear portion when viewed from the radial direction of the main sheave. τ 6. The belt type stepless speed changer of claim 1 or 2, wherein A belt type stepless speed changer as claimed in claim 6, wherein The portion accelerates the portion of the wear. The belt type stepless speed changer of claim 1 or 2, wherein the covering member is formed such that the covering The thickness of his part. 126150-1000608.doc 1351479 9. The belt type stepless speed changer of claim 1, wherein the braking portion includes a contact surface contacting the covering member, and a contact surface is formed on the contact surface and protrudes toward the pressing member The raised portion. 10. The belt type stepless speed changer of claim 2 or 9, wherein the covering member is formed such that a thickness of a portion of the covering member that is in contact with the convex portion is greater than a height of the convex portion at the main sheave The height of the radial direction. u. The belt type stepless speed changer of claim 2 or 9, wherein. The pressing member is formed in a cylindrical shape or a cylindrical shape extending in a circumferential direction of the main sheave, and the thickness of the portion of the cover member that is in contact with the convex portion is the push Press at least one percent of the outer circumferential radius of the 7L piece. 12. The belt type stepless speed changer of claim 2 or 2, wherein the pressing member body is formed in a shape of a 或^ u or a cylinder, and is formed.兀 * The outer peripheral surface of the body of the body 13. As claimed in the item "Gou 2 belt type stepless speed changer, wherein the hardness of the covering member is less than 1 A ^ a, the hardness of the body of the pressing member is pressed. Request item] or vehicle. The straddle type vehicle of the belt type stepless speed changer 15. - The type of belt type stepless change transmission includes: - the first groove wheel element #·^ pieces, the side belt type without section In the sleeve-direction of the first sheave element, the second sheave element is disposed in the first sheave element, ...: facing the /, /, the first sheave element in a displaced manner Constituting i26i50-100060S.doc *4. 1351479 - for the belt loop cover h with grooves; a main sheave of each of the seven brake portions; - a secondary sheave; and - the sleeve of the main sheave and the secondary sheave a belt 曰 and the urging member rotates about the rotating shaft as the second sheave member rotates, the radial direction of the (four) member toward the second sheave member by the centrifugal force generated during the rotating Moving outwardly and simultaneously pushing the second sheave element toward the cough first sheave element side, thereby reducing the width of the skin; Wherein the pressing member further comprises a pushing member body and a covering member covering at least a portion of the surface of the pressing member body, and the surface of the pressing member body is covered by the covering member At least a portion of the portion has a concave-convex portion including a convex portion or a concave portion that is engaged with the covering member, and the braking portion causes the belt groove to be reached by the second sheave member The smallest width of the smallest wheel ratio is in contact with the covering member of the pressing member to limit the displacement of the pressing member to the outer side of the second sheave member in the steering direction. 126150-1000608.doc